CN104329170A - Gas turbine facility - Google Patents
Gas turbine facility Download PDFInfo
- Publication number
- CN104329170A CN104329170A CN201410350604.9A CN201410350604A CN104329170A CN 104329170 A CN104329170 A CN 104329170A CN 201410350604 A CN201410350604 A CN 201410350604A CN 104329170 A CN104329170 A CN 104329170A
- Authority
- CN
- China
- Prior art keywords
- gas
- drying
- flow
- burning
- flow rate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
- F02C3/34—Gas-turbine plants characterised by the use of combustion products as the working fluid with recycling of part of the working fluid, i.e. semi-closed cycles with combustion products in the closed part of the cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/04—Air intakes for gas-turbine plants or jet-propulsion plants
- F02C7/057—Control or regulation
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Regulation And Control Of Combustion (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention relates to a gas turbine facility. A gas turbine facility 10 of an embodiment has a combustor 20 combusting fuel and oxidant, a turbine 21 rotated by combustion gas exhausted from the combustor 20, and a pipe 41 guiding a part of the combustion gas exhausted from the turbine 21 to a pipe 42 supplying the oxidant. Further, the gas turbine facility 10 has a pipe 43 guiding mixed gas constituted of the oxidant and the combustion gas to the combustor 20, a pipe 45 guiding another part of the combustion gas to the combustor 20 as working fluid of the turbine, and a pipe 40 exhausting a remaining part of the combustion gas to an outside.
Description
Technical field
The present invention relates to gas turbine equipment.
Background technique
According to requirement such as reduction carbon dioxide, saving resource etc., the high efficiency in power station is at development.Specifically, the high temperature, combined cycle etc. of the working fluid of gas turbine, steamturbine develop energetically.In addition, about the recovery technology of carbon dioxide, also constantly research and develop.
Fig. 5 is the system diagram of the existing gas turbine equipment making it circulate as working fluid a part for the carbon dioxide generated in burner (combustor).As shown in Figure 5, boosted by compressor (compressor) 310 from deaerator (not shown) isolated oxygen, and controlled flow by flow control valve 311.The oxygen that have passed through flow control valve 311 accepts the heat from combustion gas and is heated in heat exchanger 312, then supplies to burner 313.
For fuel, supplied to burner 313 by flow control valve 314 adjust flux.This fuel is hydrocarbon.Fuel and oxygen carry out reacting (burning) in burner 313.If fuel and oxygen burn, then generation carbon dioxide and water vapor are as combustion gas.The flow of fuel and oxygen becomes stoichiometric mixture ratio (theoretic mixture ratio) (stoichiometric mixture ratio) under being adjusted to the state that each leisure mixes completely.
The combustion gas generated in burner 313 are imported into turbine 315.The combustion gas of expansion work have been carried out through over-heat-exchanger 312 in turbine 315, and then through over-heat-exchanger 316.When through over-heat-exchanger 316, water vapor condensation and become water.Water is discharged to outside through pipe arrangement 319.
Carbon dioxide after being separated with water vapor is boosted by compressor 317.A part for carbon dioxide after boosting, by flow control valve 318 adjust flux, is then externally discharged.Remaining carbon dioxide is heated and is supplied to burner 313 in heat exchanger 312.
Here, the carbon dioxide supplied to burner 313 is used to the dilution of wall cooling to burner 313, combustion gas.And carbon dioxide is imported in burner 313, is imported into turbine 315 together with combustion gas.
In above-mentioned system, the carbon dioxide generated by the hydrocarbon and oxygen that are supplied to burner 313 and water are discharged to the outside of system.And remaining carbon dioxide is at system Inner eycle.
In above-mentioned existing gas turbine equipment, oxygen becomes high pressure by compressor 310, and then by becoming high temperature through over-heat-exchanger 312.When the concentration of oxygen is high and the temperature of oxygen is high temperature, the burning of the supplying tubing of accelerating oxidation agent sometimes.
In addition, due to as mentioned above, the flow of fuel and oxygen becomes stoichiometric mixture ratio, so the temperature of combustion gas becomes high temperature under being adjusted to the state that each leisure mixes completely.Therefore, the carbon dioxide generated by burning carries out thermal dissociation, is in state of equilibrium with carbon monoxide with a certain concentration.The concentration of higher then this carbon monoxide of temperature of combustion gas is higher.
If imported the high region of the concentration of this carbon monoxide by the carbon dioxide after compressor 317 boosts, then combustion temperature reduces.Thus, produce carbon monoxide and discharge this problem with not oxidized state from burner 313.
Summary of the invention
The present invention relates to gas turbine equipment, it is characterized in that, possess: make the burner that fuel and oxygenant burn; The turbine rotated by the combustion gas of discharging from described burner; To the heat exchanger that the described combustion gas of discharging from described turbine cool; From the described combustion gas that have passed through described heat exchanger, remove water vapor and become the water vapor remover of drying and burning gas; A part for described drying and burning gas is guided to the drying and burning gas supply pipe of the oxygenant supplying pipe supplying described oxygenant; The mixed gas be made up of described oxygenant and described drying and burning gas is made to guide to the mixed gas supplying pipe of described burner through described heat exchanger; It is made to guide to the working fluid supplying pipe of described burner through described heat exchanger as the working fluid of described turbine other parts of described drying and burning gas; With the discharge tube that the remainder of described drying and burning gas is discharged to the outside.
Accompanying drawing explanation
Fig. 1 is the system diagram of the gas turbine equipment of mode of execution.
Fig. 2 be when representing the mass ratio change making the relative mixed gas of oxygen, relative to the figure of the maximum combustion gas temperature of equivalent proportion (equivalence ratio).
Fig. 3 be when representing the mass ratio change making the relative mixed gas of oxygen, relative to the figure of the concentration of the carbon monoxide of equivalent proportion.
Fig. 4 is the figure having represented smooth combustion territory based on the mass ratio of the relative mixed gas of oxygen and maximum combustion gas temperature.
Fig. 5 is the system diagram of the existing gas turbine equipment making it circulate as working fluid a part for the carbon dioxide generated in the burner.
Embodiment
Gas turbine equipment possesses: the burner that fuel and oxygenant are burnt, the turbine rotated by the combustion gas of discharging from described burner, the heat exchanger cooled the described combustion gas of discharging from described turbine and remove water vapor from the described combustion gas that have passed through described heat exchanger and become the water vapor remover of drying and burning gas.Further, gas turbine equipment possesses: a part for described drying and burning gas is guided to the drying and burning gas supply pipe of the oxygenant supplying pipe supplying described oxygenant, make the mixed gas be made up of described oxygenant and described drying and burning gas guide to through described heat exchanger described burner mixed gas supplying pipe, make it guide to the working fluid supplying pipe of described burner through described heat exchanger as the working fluid of described turbine other parts of described drying and burning gas; With the discharge tube that the remainder of described drying (dry) combustion gas is externally discharged.
Below, with reference to accompanying drawing, embodiments of the present invention are described.
Fig. 1 is the system diagram of the gas turbine equipment 10 of mode of execution.As shown in Figure 1, gas turbine equipment 10 possesses: the burner 20 that fuel and oxygenant are burnt and the turbine 21 rotated by the combustion gas of discharging from this burner 20.Turbine 21 such as links generator 22.Wherein, combustion gas of discharging from burner 20 mentioned here comprise the combustion products that generated by fuel and oxygenant and to supply and from the drying and burning gas (carbon dioxide) described later that burner 20 is discharged together with combustion products to burner 20.
The combustion gas of discharging from turbine 21 are cooled by passing through from heat exchanger 23.Combustion gas after over-heat-exchanger 23 are further across heat exchanger 24.Combustion gas are removed water vapor contained combustion gas by passing through from this heat exchanger 24, become drying and burning gas.Here, water vapor passes through the condensation from heat exchanger 24 process, becomes water.Water is such as discharged to outside through pipe arrangement 46.Wherein, heat exchanger 24 plays function as the water vapor remover removed by water vapor.
A part for drying and burning gas flow into the pipe arrangement 41 of pipe arrangement 40 branch from drying and burning gas flow warp.And the flow rate regulating valve 26 that the part of drying and burning gas is located at pipe arrangement 41 adjusts flow, and import in the pipe arrangement 42 of supply oxygenant.By air-separating plant (not shown) from air isolated oxygen as oxidant stream to pipe arrangement 42.Pipe arrangement 42 is provided with the flow rate regulating valve 30 adjusted the flow of oxygenant.
Wherein, pipe arrangement 41 plays function as drying and burning gas supply pipe, and pipe arrangement 42 plays function as oxygenant supplying pipe.In addition, flow rate regulating valve 26 plays function as drying and burning gas flow regulating valve, and flow rate regulating valve 30 plays function as oxidizer flow rate regulating valve.
Here, such as use hydrocarbon as fuel, in burner 20, when making them burn when the flow of fuel and oxygen being adjusted to stoichiometric mixture ratio (equivalent proportion 1), the composition of drying and burning gas is nearly all carbon dioxide.In addition, the situation of the micro CO being such as mixed with less than 0.2% is also comprised in drying and burning gas.As hydrocarbon, such as, rock gas, methane etc. can be used.In addition, as fuel, also gasification gas etc. can be utilized.
The mixed gas be made up of oxygenant and drying and burning gas flows in pipe arrangement 43, boosted by the compressor 25 being located at pipe arrangement 43.Mixed gas after boosting is imported into burner 20 through over-heat-exchanger 23.Wherein, pipe arrangement 43 plays function as mixed gas supplying pipe.
Mixed gas obtains heat from the combustion gas of being discharged by turbine 21 and is heated in heat exchanger 23.The mixed gas being directed into burner 20 is imported into combustion zone together with the fuel supplied by pipe arrangement 44.And the oxygenant of mixed gas and fuel generation combustion reaction, generate combustion gas.Wherein, pipe arrangement 44 is provided with the flow rate regulating valve 27 that the flow of fuel that opposed firing device 20 supplies carries out adjusting.
On the other hand, the pipe arrangement 40 of the position downstream than pipe arrangement 41 branch is provided with compressor 28.Drying and burning gas beyond the drying and burning gas branching to pipe arrangement 41 in drying and burning gas is boosted by compressor 28.A part for drying and burning gas after boosting flows into the pipe arrangement 45 from pipe arrangement 40 branch.And the flow rate regulating valve 29 that the drying and burning gas flow through in pipe arrangement 45 is located at pipe arrangement 45 adjusts flow, is directed to burner 20 through over-heat-exchanger 23.Wherein, pipe arrangement 45 plays function as working fluid supplying pipe, and flow rate regulating valve 29 plays function as operative fluid flow rate regulating valve.
The drying and burning gas flowing through pipe arrangement 45 obtains heat from the combustion gas of being discharged by turbine 21 and is heated in heat exchanger 23.The drying and burning gas being directed into burner 20 is such as directed to the downstream side of the combustion zone in combustion liner from the cooling of combustion liner (liner), dilution holes etc.Because this drying and burning gas makes turbine 21 rotate together with the combustion gas generated by burning, so play function as working fluid.
On the other hand, the remaining part of the drying and burning gas after being boosted by compressor 28 is discharged to the outside from the end of pipe arrangement 40.The end of the pipe arrangement 40 of externally being discharged by drying and burning gas also plays function as discharge tube.
Gas turbine equipment 10 possesses: the flow testing division 50 detected the flow of the fuel flowing through pipe arrangement 44, the flow testing division 51 detected the flow of the oxygenant flowing through pipe arrangement 42, the flow testing division 52 detected the flow of the drying and burning gas flowing through pipe arrangement 41, the flow testing division 53 that detects the flow of the drying and burning gas (working fluid) flowing through pipe arrangement 45.Each flow testing division is such as made up of flowmeters such as Venturi tube (Venturi) formula or Coriolis-type (Colioris) formulas.
Here, flow testing division 50 plays function as fuel flow rate detection unit, flow testing division 51 plays function as oxidizer flow rate detection unit, and flow testing division 52 plays function as drying and burning detection of gas flow rate portion, and flow testing division 53 plays function as operative fluid flow rate detection unit.
Gas turbine equipment 10 possesses based on the testing signal from above-mentioned each flow testing division 50,51,52,53, to the control device 60 that the aperture of each flow rate regulating valve 26,27,29,30 controls.This control device 60 such as mainly possesses arithmetic unit (CPU), reads storage unit, the input-output units etc. such as private memory (ROM), random access storage device (RAM).In CPU, such as use the program stored by storage unit, data etc. to perform various calculation process.
Input-output unit is by external equipment input electrical signal, or external device exports electrical signal.Specifically, input-output unit and each flow testing division 50,51,52,53, each flow rate regulating valve 26,27,29,30 etc. connects into can the various signal of input output.This processing example performed by control device 60 is as by realizations such as computer installations.
Here, in the mixed gas flowing through pipe arrangement 43, preferably oxygenant is set to 15 ~ 40 quality % relative to the ratio of mixed gas.In addition, more preferably oxygenant is set to 20 ~ 30 quality % relative to the ratio of mixed gas.Wherein, mixed gas is made up of drying and burning gas (carbon dioxide) and oxygenant (oxygen).
Below, the reason preferably oxygenant (oxygen) being set to above-mentioned scope relative to the ratio of mixed gas is described.
Fig. 2 is the figure of maximum combustion gas temperature when representing the mass ratio change making oxygen relative to mixed gas, relative equivalent ratio.In fig. 2, maximum combustion gas temperature refers to adiabatic flame temperature (adiabatic flame temperature).Fig. 3 is the figure of the concentration of carbon monoxide when representing the mass ratio change making oxygen relative to mixed gas, relative equivalent ratio.In figure 3, concentration, the i.e. longitudinal axis of carbon monoxide are expressed in logarithmic.In addition, the concentration of carbon monoxide is the equilibrium composition value under the adiabatic flame temperature of each condition.Fig. 4 be based on oxygen relative to the mass ratio of mixed gas and maximum combustion gas temperature, illustrate the figure in smooth combustion territory.In the diagram, setting equivalent proportion is 1, such as, amplitude of fluctuation during the operating at ordinary times of the indicated by the solid line setting equivalent proportion caused because of flow variation etc.In addition, in the diagram, smooth combustion territory is the region becoming more than maximum combustion gas temperature in stable combustion limit.
Wherein, Fig. 2 ~ Fig. 4 uses methane (CH
4) example that calculates is carried out as fuel.In addition, the equivalent proportion in Fig. 2 and Fig. 3 is equivalent proportion when being assumed to be fuel and oxygen Homogeneous phase mixing.
As shown in Figure 2, the ratio along with oxygen becomes large, and maximum combustion gas temperature uprises.Such as, when comparing with identical equivalent proportion, to burner 20 supply fuel, oxygen, carbon dioxide flow identical.Therefore, oxygen concentration difference refers to different from the flow of the drying and burning gas (carbon dioxide) that oxygen mixes.
Such as, when the ratio of oxygen is little, the flow of mixed drying and burning gas is large.Therefore, the flow flowing into the drying and burning gas (working fluid) of burner 20 via pipe arrangement 45 diminishes.On the other hand, when the ratio of oxygen is large, the flow of mixed drying and burning gas is little.Therefore, the flow flowing into the drying and burning gas (working fluid) of burner 20 via pipe arrangement 45 becomes large.Namely known, if different from the ratio that fuel is ejected into the oxygen in the mixed gas of combustion zone together, even if then the temperature of the combustion gas in the outlet port of burner 20 is identical, the maximum combustion gas temperature (adiabatic flame temperature) in combustion zone is also significantly different.
As shown in Figure 3, the ratio along with oxygen becomes large, and the concentration of carbon monoxide increases.This is because flame temperature becomes large along with the ratio of oxygen and uprises, the equilibrium composition value of the carbon monoxide in burning territory increases.In order to the concentration making carbon monoxide is below permitted value, the ratio making oxygen is needed to be below 40 quality %.From the view point of the concentration reducing carbon monoxide further, more preferably the ratio of oxygen is set to below 30 quality %.Wherein, the permitted value of the concentration of carbon monoxide is such as set to obtain the concentration specifying above combustion efficiency.
By the ratio of oxygen is set to below 40 quality %, even if such as when the oxidation of carbon monoxide is not promoted by the drying and burning gas being directed into the downstream side of the combustion zone in combustion liner from dilution holes etc., the concentration of the carbon monoxide contained by combustion gas also can be reduced.
In order to maintain stable burning in burning territory, needing maximum combustion air temperature settings is more than the temperature of stable combustion limit.As shown in Figure 4, setting equivalent proportion is 1, when considering amplitude of fluctuation, needs the ratio of oxygen to be more than 15 quality %.In order to obtain more stable burning, more preferably the ratio of oxygen is set to more than 20 quality %.
Here, the maximum combustion gas temperature that stable combustion limit such as occurs to dissipate based on bad stability or the flame of flame sets.
Result according to Fig. 2 ~ Fig. 3, in order to maintain stable burning and reduce the concentration of carbon monoxide, the ratio of the relative mixed gas of preferred oxidant is 15 ~ 40 quality %.In addition, more preferably oxygenant is set to 20 ~ 30 quality % relative to the ratio of mixed gas.
In addition, in pipe arrangement 43, the situation that combination drying combustion gas (carbon dioxide) flow can suppress the oxidation of pipe arrangement compared with pure oxygen with flowing through.
Here, such as when according to mix in the oxygenant that have passed through heat exchanger 23 from heat exchanger 23 through before the mode of drying and burning gas constitute pipe arrangement, be blown into cryogen to high temperature fluid.Therefore, the pipe arrangement of mixing unit produces thermal stress sometimes.In addition, such as, when according to pipe arrangement 45 branch is constituted pipe arrangement to the mode of the drying and burning gas of oxygenant mixing after over-heat-exchanger 23 that have passed through heat exchanger 23, arm is needed to possess flow control valve.But, owing to flowing through the drying and burning gas of high temperature in arm, so the valve of use high temperature of having to, cause equipment cost to increase.
Given this, as shown in Figure 1, by pipe arrangement being configured to make oxygenant lean on upstream side with the position of drying and burning gas and vapor permeation than heat exchanger 23, can preventing in the pipe arrangement of mixing unit, producing excessive stresses, equipment cost increases.
Next, the mixed gas be made up of oxygen and drying and burning gas (carbon dioxide) supplied with reference to Fig. 1 opposed firing device 20, fuel, the action related to as the flow adjustment of the drying and burning gas (carbon dioxide) of working fluid are described.
When gas turbine equipment 10 operates, control device 60 is transfused to the output signal from flow testing division 50 via input-output unit.Based on the output signal be transfused to, the program, data etc. that store in use storage unit calculate the oxygen flow in order to equivalent proportion be set to required for 1 in arithmetic unit.Wherein, fuel flow rate such as controls the valve opening adjustment of flow rate regulating valve 27 by exporting based on the gas turbine be required.
Here, in gas turbine equipment 10, preferably from the combustion gas that burner 20 is discharged, do not retain unnecessary oxygenant (oxygen), fuel.Given this, the flow adjustment of the fuel supplied to burner 20 and oxygen is become stoichiometric mixture ratio (equivalent proportion 1).
Then, control device 60, based on the output signal from flow testing division 51 inputted by input-output unit, exports from input-output unit to flow rate regulating valve 30 and is used for the output signal of regulating valve aperture, to flow the oxygen flow calculated to pipe arrangement 42.
Then, in the arithmetic unit of control device 60, based on the output signal from flow testing division 51 inputted by input-output unit, become the mode of setting value according to oxygenant relative to the ratio of mixed gas, calculate the flow of the drying and burning gas (carbon dioxide) mixed in oxygen.Here, setting value is set to 15 ~ 40 quality % as described above.
Then, control device 60 is based on the output signal from flow testing division 52 inputted by input-output unit, export from input-output unit to flow rate regulating valve 26 and be used for output signal that valve opening is adjusted, to flow the carbon dioxide flow calculated to pipe arrangement 41.
Then, in the arithmetic unit of control device 60, based on the output signal from flow testing division 50 and flow testing division 52 inputted by input-output unit, calculate the flow of the drying and burning gas (carbon dioxide) supplied to burner 20 as working fluid.In addition, the flow of drying and burning gas (carbon dioxide) also can be calculated based on the output signal from flow testing division 51 and flow testing division 52.
Here, as described above, such as, flow based on the carbon dioxide flow through in the flow of the fuel supplied to burner 20 and pipe arrangement 41 decides the flow of the drying and burning gas (carbon dioxide) supplied as working fluid.Such as, externally discharge from the terminal of pipe arrangement 40 playing function as discharge tube and burner 20, make fuel combustion and the suitable amount of the growing amount of carbon dioxide that generates.Like this, when the constant flow of fuel, such as, be constant by the flow control of carbon dioxide to the supply of burner 20 entirety.That is, when the constant flow of fuel, the carbon dioxide of constant flow rate is at system Inner eycle.
Then, control device 60 is based on the output signal from flow testing division 53 inputted by input-output unit, the output signal be used for valve opening adjusts is exported from input-output unit to flow rate regulating valve 29, so that the flow of the carbon dioxide calculated that flows to pipe arrangement 45.
Control as described above, the mixed gas be made up of oxygen and drying and burning gas (carbon dioxide), fuel, to be supplied by burner 20 as the drying and burning gas (carbon dioxide) of working fluid.By carrying out such control, even if such as when there occurs load change etc., the mass ratio of the oxygen in mixed gas also can be made constant, make the flow of the carbon dioxide supplied to burner 20 also constant simultaneously.
As mentioned above, according to the gas turbine equipment 10 of mode of execution, by mixing a part for the combustion gas (drying and burning gas) after eliminating water vapor to oxygenant and supplying to burner 20, burning gas temperature can be made to reduce.Thus, in burner 20, the growing amount of the carbon monoxide generated because of the thermal dissociation of carbon dioxide can be suppressed, the concentration of carbon monoxide is reduced.In addition, by oxygenant (oxygen) combination drying combustion gas (carbon dioxide), the oxidation of pipe arrangement can be suppressed.
According to mode of execution described above, the oxidation of the supplying tubing of oxygenant can be suppressed, and reduce the discharge concentration of carbon monoxide.
Be illustrated concrete mode of the present invention above, but the present invention is not limited thereto, those skilled in the art can carry out various additional, change for above-mentioned mode certainly without departing from the scope of the subject in the invention, and these all belong to scope of the present invention.The content of scope of the present invention only described in technological scheme limits.
Claims (7)
1. a gas turbine equipment, is characterized in that, possesses:
Make the burner that fuel and oxygenant burn;
The turbine rotated by the combustion gas of discharging from described burner;
To the heat exchanger that the described combustion gas of discharging from described turbine cool;
From the described combustion gas that have passed through described heat exchanger, remove water vapor and become the water vapor remover of drying and burning gas;
A part for described drying and burning gas is guided to the drying and burning gas supply pipe of the oxygenant supplying pipe supplying described oxygenant;
The mixed gas be made up of described oxygenant and described drying and burning gas is guided to the mixed gas supplying pipe of described burner through described heat exchanger;
Using the working fluid of other parts of described drying and burning gas as described turbine, and guide to the working fluid supplying pipe of described burner through described heat exchanger; With
By the discharge tube that the remainder of described drying and burning gas is discharged to the outside.
2. gas turbine equipment according to claim 1, is characterized in that,
Described oxygenant is 15 ~ 40 quality % relative to the ratio of described mixed gas.
3. gas turbine equipment according to claim 1, is characterized in that also possessing:
Fuel flow rate detection unit, detects the flow of the described fuel supplied to described burner;
Oxidizer flow rate detection unit, detects the flow of the described oxygenant flow through in described oxygenant supplying pipe;
Oxidizer flow rate regulating valve, adjusts the flow of the described oxygenant flow through in described oxygenant supplying pipe; With
Control device, based on the testing signal from described fuel flow rate detection unit and described oxidizer flow rate detection unit, controls the aperture of described oxidizer flow rate regulating valve.
4. gas turbine equipment according to claim 3, is characterized in that also possessing:
Drying and burning detection of gas flow rate portion, detects the flow of the described drying and burning gas flow through in described drying and burning gas supply pipe; With
Drying and burning gas flow regulating valve, adjusts the flow of the described drying and burning gas flow through in described drying and burning gas supply pipe,
Described control device, based on the testing signal from described oxidizer flow rate detection unit and described drying and burning detection of gas flow rate portion, controls the aperture of described drying and burning gas flow regulating valve.
5. gas turbine equipment according to claim 4, is characterized in that also possessing:
Operative fluid flow rate detection unit, detects the flow of the described working fluid flow through in described working fluid supplying pipe; With
Operative fluid flow rate regulating valve, adjusts the flow of the described working fluid flow through in described working fluid supplying pipe,
Described control device, based on the testing signal from described fuel flow rate detection unit, described drying and burning detection of gas flow rate portion and described operative fluid flow rate detection unit, controls the aperture of described operative fluid flow rate regulating valve.
6. gas turbine equipment according to claim 1, is characterized in that,
Described fuel is hydrocarbon, and described oxygenant is oxygen.
7. gas turbine equipment according to claim 1, is characterized in that,
Described drying and burning gas is carbon dioxide.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710716728.8A CN107605599B (en) | 2013-07-22 | 2014-07-22 | Gas turbine plant |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013-151790 | 2013-07-22 | ||
| JP2013151790A JP6220586B2 (en) | 2013-07-22 | 2013-07-22 | Gas turbine equipment |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710716728.8A Division CN107605599B (en) | 2013-07-22 | 2014-07-22 | Gas turbine plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104329170A true CN104329170A (en) | 2015-02-04 |
| CN104329170B CN104329170B (en) | 2017-09-08 |
Family
ID=52342456
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710716728.8A Expired - Fee Related CN107605599B (en) | 2013-07-22 | 2014-07-22 | Gas turbine plant |
| CN201410350604.9A Expired - Fee Related CN104329170B (en) | 2013-07-22 | 2014-07-22 | Gas turbine equipment |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710716728.8A Expired - Fee Related CN107605599B (en) | 2013-07-22 | 2014-07-22 | Gas turbine plant |
Country Status (4)
| Country | Link |
|---|---|
| US (2) | US20150020497A1 (en) |
| JP (1) | JP6220586B2 (en) |
| CN (2) | CN107605599B (en) |
| CA (1) | CA2856993C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10526968B2 (en) | 2015-12-22 | 2020-01-07 | Toshiba Energy Systems & Solutions Corporation | Gas turbine facility |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6220586B2 (en) * | 2013-07-22 | 2017-10-25 | ８ リバーズ キャピタル，エルエルシー | Gas turbine equipment |
| JP6220589B2 (en) * | 2013-07-26 | 2017-10-25 | ８ リバーズ キャピタル，エルエルシー | Gas turbine equipment |
| JP6250332B2 (en) | 2013-08-27 | 2017-12-20 | ８ リバーズ キャピタル，エルエルシー | Gas turbine equipment |
| JP6384916B2 (en) * | 2014-09-30 | 2018-09-05 | 東芝エネルギーシステムズ株式会社 | Gas turbine equipment |
| MA40950A (en) | 2014-11-12 | 2017-09-19 | 8 Rivers Capital Llc | SUITABLE CONTROL SYSTEMS AND PROCEDURES FOR USE WITH POWER GENERATION SYSTEMS AND PROCESSES |
| US11686258B2 (en) | 2014-11-12 | 2023-06-27 | 8 Rivers Capital, Llc | Control systems and methods suitable for use with power production systems and methods |
| US10961920B2 (en) | 2018-10-02 | 2021-03-30 | 8 Rivers Capital, Llc | Control systems and methods suitable for use with power production systems and methods |
| JP2016151425A (en) * | 2015-02-16 | 2016-08-22 | パナソニックＩｐマネジメント株式会社 | Radar system |
| AU2015275260B2 (en) * | 2015-12-22 | 2017-08-31 | Toshiba Energy Systems & Solutions Corporation | Gas turbine facility |
| WO2017145094A1 (en) | 2016-02-26 | 2017-08-31 | 8 Rivers Capital, Llc | Systems and methods for controlling a power plant |
| CN109415953B (en) * | 2016-04-21 | 2021-08-06 | 八河流资产有限责任公司 | System and method for oxidizing hydrocarbon gases |
| BR112019018466A2 (en) | 2017-03-07 | 2020-04-14 | 8 Rivers Capital Llc | system and method for operating a flexible fuel combustor for a gas turbine |
| WO2019167021A1 (en) | 2018-03-02 | 2019-09-06 | 8 Rivers Capital, Llc | Systems and methods for power production using a carbon dioxide working fluid |
| WO2020021456A1 (en) * | 2018-07-23 | 2020-01-30 | 8 Rivers Capital, Llc | System and method for power generation with flameless combustion |
| KR102113799B1 (en) | 2018-10-25 | 2020-05-21 | 한국에너지기술연구원 | System and Method for Direct-Fired Supercritical CO2 Power Generation of Sub-MWe |
| AU2020369233A1 (en) | 2019-10-22 | 2022-05-19 | 8 Rivers Capital, Llc | Control schemes for thermal management of power production systems and methods |
| JP2023001633A (en) * | 2021-06-21 | 2023-01-06 | 東芝エネルギーシステムズ株式会社 | Operation method of gas turbine combustor |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1898499A (en) * | 2003-12-23 | 2007-01-17 | 阿尔斯通技术有限公司 | Thermal power plant with sequential combustion and reduced co2 emissions and method for operating a plant of this type |
| CN101201171A (en) * | 2006-12-11 | 2008-06-18 | 通用电气公司 | Method and system for reducing CO2 emissions in a combustion stream |
| CN101324203A (en) * | 2007-06-13 | 2008-12-17 | 通用电气公司 | Systems and methods for power generation with exhaust gas recirculation |
| US20100326084A1 (en) * | 2009-03-04 | 2010-12-30 | Anderson Roger E | Methods of oxy-combustion power generation using low heating value fuel |
| WO2012003079A1 (en) * | 2010-07-02 | 2012-01-05 | Exxonmobil Upstream Research Company | Stoichiometric combustion of enriched air with exhaust gas recirculation |
Family Cites Families (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4434613A (en) * | 1981-09-02 | 1984-03-06 | General Electric Company | Closed cycle gas turbine for gaseous production |
| DE4303174A1 (en) * | 1993-02-04 | 1994-08-18 | Joachim Dipl Ing Schwieger | Method for the generation of electrical energy |
| US5724805A (en) * | 1995-08-21 | 1998-03-10 | University Of Massachusetts-Lowell | Power plant with carbon dioxide capture and zero pollutant emissions |
| EP0859136A1 (en) * | 1997-02-17 | 1998-08-19 | N.V. Kema | Gas turbine with energy recovering |
| DE69931548T2 (en) * | 1998-04-07 | 2007-05-10 | Mitsubishi Heavy Industries, Ltd. | turbine plant |
| US6513318B1 (en) * | 2000-11-29 | 2003-02-04 | Hybrid Power Generation Systems Llc | Low emissions gas turbine engine with inlet air heating |
| EP2158388B1 (en) * | 2007-06-19 | 2019-09-11 | Ansaldo Energia IP UK Limited | Gas turbine system having exhaust gas recirculation |
| US8051654B2 (en) * | 2008-01-31 | 2011-11-08 | General Electric Company | Reheat gas and exhaust gas regenerator system for a combined cycle power plant |
| AU2009228283B2 (en) * | 2008-03-28 | 2015-02-05 | Exxonmobil Upstream Research Company | Low emission power generation and hydrocarbon recovery systems and methods |
| US8397482B2 (en) * | 2008-05-15 | 2013-03-19 | General Electric Company | Dry 3-way catalytic reduction of gas turbine NOx |
| US9297306B2 (en) * | 2008-09-11 | 2016-03-29 | General Electric Company | Exhaust gas recirculation system, turbomachine system having the exhaust gas recirculation system and exhaust gas recirculation control method |
| CA2737133C (en) * | 2008-10-14 | 2017-01-31 | Exxonmobil Upstream Research Company | Methods and systems for controlling the products of combustion |
| US8596075B2 (en) * | 2009-02-26 | 2013-12-03 | Palmer Labs, Llc | System and method for high efficiency power generation using a carbon dioxide circulating working fluid |
| US9410481B2 (en) * | 2010-09-21 | 2016-08-09 | 8 Rivers Capital, Llc | System and method for high efficiency power generation using a nitrogen gas working fluid |
| EP2444631A1 (en) * | 2010-10-19 | 2012-04-25 | Alstom Technology Ltd | Power plant and method for its operation |
| US8813472B2 (en) * | 2010-10-21 | 2014-08-26 | General Electric Company | System and method for controlling a semi-closed power cycle system |
| US20120023954A1 (en) * | 2011-08-25 | 2012-02-02 | General Electric Company | Power plant and method of operation |
| US20130145773A1 (en) * | 2011-12-13 | 2013-06-13 | General Electric Company | Method and system for separating co2 from n2 and o2 in a turbine engine system |
| US20130269356A1 (en) * | 2012-04-12 | 2013-10-17 | General Electric Company | Method and system for controlling a stoichiometric egr system on a regenerative reheat system |
| JP6220586B2 (en) * | 2013-07-22 | 2017-10-25 | ８ リバーズ キャピタル，エルエルシー | Gas turbine equipment |
-
2013
- 2013-07-22 JP JP2013151790A patent/JP6220586B2/en active Active
-
2014
- 2014-07-15 US US14/331,361 patent/US20150020497A1/en not_active Abandoned
- 2014-07-16 CA CA2856993A patent/CA2856993C/en active Active
- 2014-07-22 CN CN201710716728.8A patent/CN107605599B/en not_active Expired - Fee Related
- 2014-07-22 CN CN201410350604.9A patent/CN104329170B/en not_active Expired - Fee Related
-
2020
- 2020-03-20 US US16/825,888 patent/US20200284189A1/en not_active Abandoned
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1898499A (en) * | 2003-12-23 | 2007-01-17 | 阿尔斯通技术有限公司 | Thermal power plant with sequential combustion and reduced co2 emissions and method for operating a plant of this type |
| CN101201171A (en) * | 2006-12-11 | 2008-06-18 | 通用电气公司 | Method and system for reducing CO2 emissions in a combustion stream |
| CN101324203A (en) * | 2007-06-13 | 2008-12-17 | 通用电气公司 | Systems and methods for power generation with exhaust gas recirculation |
| US20100326084A1 (en) * | 2009-03-04 | 2010-12-30 | Anderson Roger E | Methods of oxy-combustion power generation using low heating value fuel |
| WO2012003079A1 (en) * | 2010-07-02 | 2012-01-05 | Exxonmobil Upstream Research Company | Stoichiometric combustion of enriched air with exhaust gas recirculation |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10526968B2 (en) | 2015-12-22 | 2020-01-07 | Toshiba Energy Systems & Solutions Corporation | Gas turbine facility |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104329170B (en) | 2017-09-08 |
| CA2856993A1 (en) | 2015-01-22 |
| JP2015021465A (en) | 2015-02-02 |
| US20150020497A1 (en) | 2015-01-22 |
| CN107605599B (en) | 2020-01-14 |
| CA2856993C (en) | 2017-08-29 |
| US20200284189A1 (en) | 2020-09-10 |
| CN107605599A (en) | 2018-01-19 |
| JP6220586B2 (en) | 2017-10-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104329170A (en) | Gas turbine facility | |
| US10495306B2 (en) | Methods and systems for controlling the products of combustion | |
| CN104343537B (en) | Gas-turbine plant | |
| CA2906503C (en) | Gas turbine facility | |
| JP7084939B2 (en) | Systems and methods for operating flexible fuel combustors for gas turbines | |
| JP2015045246A (en) | Gas turbine installation | |
| US9476588B2 (en) | Boiler and operating method of same | |
| JP2018048646A (en) | Gas turbine installation |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C41 | Transfer of patent application or patent right or utility model | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20151216 Address after: North Carolina Applicant after: 8 RIVERS CAPITAL, LLC Address before: Tokyo, Japan Applicant before: Toshiba Corp. |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20170908 Termination date: 20210722 |